F hawthorne



Oct. 13, 1959 N. F. HAWTHORNE 2,908,441

TENS-TRANSFER MECHANISM FOR A DUPLEX CALCULATING MACHINE Filed March 14"I 1955 7 Sheets-Sheet 1 Oct. 13, 1959 N. F. HAWTHORNE 2,903,441

TENS-TRANSFER MECHANISM FOR A DUPLEX CALCULATING MACHINE Filfld March 14, 1955 7 Sheets-Sheet 2 V Iv Nb k mw Oct. 13, 1959 N. F. HAWTHORNE 2,903,441

TENS-TRANSFER MECHANISM FOR A DUPLEX CALCULATING MACHINE med larch 14. 1955 7 Sheets-Sheet 3 Oct. 13, .1959

N. F. HAWTHORNE TENS-TRANSFER MECHANISM FOR A DUPLEX CALCULATING MACHINE Filed March 14, 1955 7 Sheets-Sheet 4 km m Oct. 13, 1959 N. F. HAWTHORNE ,9

TENS-TRANSFER MECHANISM FOR A DUPLEX CALCULATING MACHINE Filed March 14, 1955 7 Sheets-Shet 5 FII5 EI Oct. 13, 1959 N. F. HAWTHORNE 2,903,441

TENS-TRANSFER MECHANISM FOR A DUPLEX CALCULATING MACHINE Filed March 14, 1955 7 Sheets-Sheet 6 @@@m@w@w@% 2,908,441 Patented Oct. 13, 1959 TENS-TRANSFER MECHANISM FOR A DUPLEX CALCULATING MACHINE Nathaniel F. Hawthorne, Alameda, Calif., assignor to Friden, Inc., a corporation of California Application March 14, 1955, Serial No. 493,857 7 Claims. (Cl. 235-138) This invention relates to calculating machines and more particularly to an improved calculating machine of the Thomas-type, such as shown in the Patent No. 2,229,889, issued to Carl M. Friden, January 28, 1941. However, the machine in which this invention is incorporated is provided with two similar registers selectively or simultaneously operable to register values under the control of a single unicyclically operable actuating mechanism, as disclosed in the copending application of Nils H. Bergfelt, S.N. 458,883, filed September 28, 1954, issued as Patent No. 2,893,631 on July 7, 1959.

The tens-transfer mechanism for one register is of the conventional type disclosed in the Patents No. 2,273,857, issued to Carl M. F. Friden, and No. 2,306,247, issued to Carl M. Friden, et al., while that of the second register is of an improved type effective to increase the transfer capacity of a machine.

It is a general object of the invention to provide an improved tens-transfer mechanism for calculating machines.

Another object of the invention register simultaneously with the register.

Another object of the invention is to provide an improved tens-transfer mechanism in a register of a duplex calculating machine having a single unidirectional cyclically operable actuating mechanism disengageable from one register during the transfer in either or both registers.

Another object of the invention is to provide a duplex calculating machine, embodying a single unidirectional actuating mechanism, with an improved tens-transfer mechanism effective with plus or minus registrations in one register irrespective of the sign character'of registrations in the other register.

A further object of the invention is to provide an improved tens-transfer mechanism which can be readily incorporated to provide extra transferring orders in a calculating machine.

Another object of the invention is to provide a register of a calculating machine with an improved tens-transfer mechanism, which, upon initiation thereof, is positively operated and immediately locked during the restoration thereof.

Other objects and advantages will become apparent from the following description of the preferred embodiment of my invention as illustrated in the accompanying tens-transfer in a second drawings in which:

Fig. 1 is a longitudinal sectional elevational view of the rear portion of the machine;

Fig. 2 is a sectional plan view taken immediately below the registers showing the transfer initiating mechanism, the view being taken on line 2-2 of Fig. 1;

Fig. 3 is a fragmentary sectional elevational view of the rear portion of the machine showing the digitation control and transfer mechanism associated with the upper register;

Fig. 4 is a plan view of the digitation disabling mechanism for the units and tens orders of the machine, the view being taken on line 44 of Fig. 3;

Fig. 5 is an elevational view from the rear of the machine showing the disengaging mechanism for the clutches controlling digitation in the upper register from the ten keyboard orders, the view being taken on line 55 of Fig. 3;

Fig. 6 is a perspective of the transfer mechanism associated with the tens order in the upper register and shown in the full-cycle position thereof;

Fig. 7 is a perspective of the transfer mechanism shown in effective position;

8 is a similar perspective View of the transfer mechanism showing the restore phase while the transfer actuator is held in operative position;

Fig. 9 is a fragmentary plan View of the transfer actuating and restore levers associated with the higher orders of the machine;

Fig. 10 is a View of the transfer control cam assembly and the relative angular position of the cams in the assembly; and

Fig. 11 is a timing chart indicating the digitation phase and the transfer phase in both registers.

Generally, a machine of the type disclosed includes a body in which the selecting, digitation, and transfer actuating mechanisms are mounted, and a shiftable register carriage which also supports a part of these transfer mechanisms.

iln the calculating machine selected for purposes of illustration, the body of the calculating machine includes side frame 10 (Fig. 1) from which a plurality of transverse brackets 11, 12, 13, 14, 15 and 16 (Figs. 1, 3 and 9) extend to a similar side frame, not shown, at the opposite or right-hand side of the machine, as viewed from the front. The side frame plates are carried by a suitable base, not shown, in the usual manner. The register carriage, indicated generally at 17, is mounted for endwise shifting movement under the control of any suitable means by rollers 18 on bracket 14, bar 19 on bracket 11, and at its rear by a shaft, not shown.

Carriage 17 (Fig. 1) comprises frames 20 and 21 supported between similar end frames 22. Each frame 20, 21 carries respective numeral wheel shafts 23, 24 ordinally arranged therein. At the upper end thereof, each of shafts 23 and 24 carries respective numeral wheels 25 and 26 having the digits from 0 to 9 inscribed thereon in the conventional manner, and, at their lower ends, the shafts carry respective IO-tooth numeral wheel gears 27 and 28. Intermediate the ends thereof, each of shafts 23, 24 carries respective star wheels 29 and 30 with which spring-urged balls 31 and 32 cooperate to maintain numeral wheels 25, 26 in adjusted position. Shafts 23 and 24 also carry respective resetting gears 33 and 34 for cooperation with suitable resetting means, not shown.

Numeral wheels 25 (Fig. 1) are rotatable in either direction to register positive and negative values, and, for this purpose, gear 2'7 has associated therewith a pair of opposed bevel gears 40, 41 formed at the ends of spool 42. The shifted positions of gears 40, 41 are controlled by transversely extending gate 43 positioned between each pair of gears 4h, 41 of the various orders of the machine. Gate 43 may be mounted in a convenient manner on similar arms 44 secured on shaft 45 for movement foiwardly and rearwardly of its central neutral position shown in Fig. 1 to engage gears 41 or 40 with numeral wheel gears 27. Thus, if gears 40 are engaged with gears 27, positive actuation of the associated numeral wheels 25 will occur, and conversely, if gears 41 are engaged with gears 27, negative actuation of numeral wheels 25 is determined. Similarly, numeral wheels 26 are rotatable in either direction to register positive and negative values by the selective engagement J of bevel gears 45 or 46 secured on either end of spool 47 with numeral wheel gears 28. The shifted position of gears 4-5, 46 are controlled by transversely extending gate 48 positioned between each pair of gears 45, 46 of the various orders of the machine. Gate 48 is mounted on similar arms '49 secured on either end of a transverse shaft for controlling the forward or rearward movement of spools 47, thereby determining the sign character of registrations in numeral wheels 26. Each of the gates 43 and 48 may be selectively controlled for movement in either direction from the centralized position, or for simultaneous movement of both in the same or in opposite directions, as disclosed in the afore-mentioned Patent No. 2,893,631.

From the above description it is seen that an increment of movement of spools 42 and 47 will be transmitted to the associated respective numeral wheels 25 and 26 if either pair of gears 40, 41 or 45, 46 are moved to active position. 7

Means are provided in the various orders of the machine to determine the number of increments of such movement. For this purpose a bank of numeral keys 54 (Fig. 1) is provided for each order of the machine, only a part of one of such banks being shown in Fig. 1. The numeral keys 54 of each bank of the machine cooperate with a pair of differential value selecting slides 55, 56 in alternate orders of the machine and selecting slides 57, 58 in the remaining orders. Each of these slides is mounted for endwise shifting movement and is provided with cam surfaces of varying inclination to be set differentially in accordance with the value of the depressed numeral key. At their rearward ends, slides 55, 56 and 57, 58 (Fig. 1) carry respective -tooth gears 59, 60 and 61, 62 which cooperate respectively with each set of stepped teeth 63, 64 and 65, 66 on actuating cylinders 67 and 68 of the digitation actuating mechanism.

Gears 59, 60 and 61, 62 are mounted for sliding movement on adjacent square shafts 72, having their front ends journalled in bracket 13 and extending rcarwardly through bracket 12, spool 42 and beyond a journal in bracket 11. Teeth 63 on actuating cylinders 67 cooperate with gears 59 in their relatively adjusted positions to determine movement of the shafts 72 for from one to five increments, while teeth 64 and gears 60 cooperate to determine movement of shafts 72 for from six to nine increments. Likewise, teeth 65 and 66 on cylinders 68 cooperate with respective gears 61 and 62 on the adjacent shafts 72 in a similar manner. A broached cylinder 73 is provided at its one end with an annular flange 74 and at its other end with a pilot gear 75 and is slidably and nonrotatably mounted on the rearwardly extended portion of each square shaft 72 for a purpose to be hereinafter described. Each pilot gear 75 is normally enmeshed with corresponding idler gear 76 rotatably mounted on a stud in bracket 11, which idler gear is, in turn, enmeshed with a gear 77 secured on each square shaft 78. At its forward end, each shaft 78 is journalled in bracket [11 and extends rearwardly through spool 47 having its rearward end journalled in bracket 16 (Figs. 1 and 3). The axis of each shaft 7 8 is disposed above, and parallel to, the axis of the corresponding one of each of shafts 72. Thus, each increment of movement transmitted to shaft 72 is also transmitted through gears 75, 76, and 77 to square shaft 78.

A pair of cylinders 67, 68 are mounted on each of filVe actuating shafts 79 for a pair of adjacent orders, the respective shafts 72 of each of such adjacent orders be ing spaced to either side of, and above, the associated actuating shaft 79. Each actuating shaft 79 is journalled in transverse brackets 1-3 and 8t] and at its front end has a bevel gear connection 81 with transverse drive shaft 82. Shaft 82 has its ends journalled in respective side frames and is driven cyclically from a suitable source of power, such as .an electric motor. In .the embodiment 4 l shown,.one cycle of operation is effected by one rotation of shaft 82. Thus, for each rotation of shaft 82, shafts 79 and cylinders 67, 68 also receive a single rotation to cause registration of the number selected by the depressed numeral keys 54 selectively or simultaneously on the associated numeral wheels 25, 26. The angularl-y disposed position of the cylinders 67, 68 on the two right-hand actuator shafts 79 is such, that when numeral keys of the same denomination are depressed in the four lower keyboard orders, rotation of shafts 79 will impart similar simultaneous increments of movement to the corresponding shafts 72. The cylinders 67, 68 on the third actuator shaft 79 from the right side of the machine, are angularly offset ten degrees from those on the first and second shafts 79 and the pair of cylinders on each shaft 79 to the left thereof is offset ten degrees from the adjacent shaft on the right. Thus, it becomes apparent that if all keys 54 representing 1 are depressed, the four lower order shafts 72 will receive a simultaneous increment of movement, while the respective pair of shafts 72 associated with the fifth and sixth orders, the seventh and eighth orders, and the ninth and tenth orders will suecessively receive an increment of movement ten degrees later than the adjacent pair of shafts to the right. The cyclic timing for each pair of cylinders 67, 68 during the digitation phase of each machine cycle is more clearly indicated in the chart shown in Fig. 11.

Conventional means are provided for preventing overthrow of the numeralwheels at the end of an actuation thereof and for this purpose the two sets of stepped teeth 63, 64 and 65, 66 (Fig. 1) of the respective cylinders 67, 68 are located with their last active teeth in alignment, and there is associated with each shaft 72, a Geneva wheel 86 mounted thereon for rotation therewith, and associated with each Geneva wheel 86 is a locking disk 87 on an actuating shaft 79. Each disk 87 is provided with a recessed portion extending around its periphery for a distance corresponding to the distance occupied by teeth 64, 66 of respective cylinders 67, 68. Each Geneva wheel 86 has ten concave faces for cooperation with the associated disk 87 so that for each increment of movement imparted to shaft 72 and the corresponding Geneva wheel 86 by one of the teeth of cylinders 67 and 68, one of the faces is positioned for cooperation with the associated disk 87. The trailing edge of the recessed portion moves into engagement with Geneva wheel 86 immediately after the last active tooth of teeth 63, 64 and 65, 66 has actuated one of the gears 59 or 60 and 61 or 62 so that the associated shaft 72, and consequently the associated numeral wheels 25 and/ or 26, are positively locked against further rotation. To centralize the shafts 72 and'Geneva wheels 86 in position after movement thereof, each shaft 72 carries a star wheel 88 adjacent frame bracket 11 engaged by a spring-pressed ball 89 mounted in bar 19.

Each pair of locking disks 87 for adjacent orders of the machine are mounted on each actuating shaft 79 in axially offset relation to the mounting of the associated actuating cylinders 67, 68.

Cyclically operable transfer mechanism of conventional construction is provided for cooperation with the actuating cylinders described above, and generally, such transfer mechanism comprises tripping means associated with each numeral wheel 25 in carriage frame 20, except that of highest order, for enabling a drive connection from a transfer actuator to the numeral wheel of the next higher order, so that such next higher order numeral wheel receives one increment of movement when the numeral wheel of lower order passes from 9 to 0 or 0 to 9. The sign character of the transferred increment is determined in the same manner as the sign character of the digitation increments. Since the transfer mechanism for numeral wheels 25 is conventional, only a brief description will herein be given. However, for a more complete disclosure, reference is to be had to the aforementioned Patent No. 2,306,247.

To effect the tripping of a transfer, each numeral wheel shaft 23 (Figs. 1 and 2) is provided with single tooth gear 92 immediately below carriage frame 20 for cooperation with tripping lever 93 pivoted at 94 in frame 20, and yieldably held therein by spring-pressed ball 95 engaging a slightly off-center seat in pivot 94. Lever 93 has extension 96 positioned in the path of single tooth gear 92 of one order, so that when the numeral wheel passes from 9 to 0 or 0 to 9 extension 96 is engaged by the tooth of gear 92, and lever 93 is rocked in a counter-clockwise direction as viewed in Fig. 2. The counter-clockwise rocking of lever 93 is against the urgency of spring-pressed ball 95 which yieldably maintains the lever in the position shown in Fig. 2.

Lever 93 is also provided with arm 97 extending into the next higher order of the machine and normally engaging lever 93 of such order adjacent its pivot 94. Arm 97 has bent end 98 (Figs. 1 and 2) which extends downwardly and engages rearwardly of annular flange 99 of gear hub 100. Hub 100 carries transfer gear 101 and is slidably mounted on shaft 72, so that rocking movement of tripping lever 93 results in shifting hub 100' and gear 101 forwardly of the machine to position gear 101 in operative relation with respect to the transfer actuator therefor. Single tooth cyclic transfer actuator 102 for gear 101 in one order is suitably mounted with single tooth actuator 102a for gear 101 of the adjacent higher order by locking disks 87. To enable movements of shaft 72 by operation of actuator 162 and to prevent overthrow thereafter, the associated locking disk 87 is provided with a transfer notch spaced from the recessed portion therein by an interposed solid portion of disk 87.

From the above description, it is seen that each time a transfer is determined in one order of the machine, gear 101 of the next higher order is moved into active position to be subsequently operated by the associated transfer actuators 102 or 10211.

Means are provided for resiliently maintaining gear 101 in either shifted position thereof, and associated with such maintaining means is a restoring cam 103, which cooperates with each pair of adjacent gears 101. Hub 100 (Fig. 1) has a second annular flange 104 which extends between spaced annular flanges 105 on shaft 106 slidably mounted in transverse bracket 8% and transverse member 107 spaced from bracket Sti and suitably supported in the framework of the machine. Shaft 106 is suitably resiliently detented in either shifted position thereof. It will be noted that when gear 181 is moved to operative position, the forward end of shaft 106 will project forwardly of bracket 80 and into the path of restoring cam 103, preferably formed integrally with actuator 102a of each pair of associated transfer actuators. The single tooth actuators 1102, 192a of each pair of actuators on the remaining actuating shafts 79 are spaced apart an angular distance to provide for successive operation of the transfer actuators from the lowest to the highest orders.

Referring to Fig. 11, it can be seen that the digitation phase of each machine cycle constitutes 165 of the cycle wherein the simultaneous digitation in the first four right-hand, or lower, orders is terminated after 135 of each cycle; and digitation in each successive pair of orders through the tenth is terminated successively ten degrees later. Immediately following the digitation phase of each cycle of operation of the machine, i.e., after 165, the pilot gears 75 associated with each of the four lower order shafts '72 are disengaged from the associated idler gears 76, thereby enabling the initiation of the transfer phase in numeral wheel dials 25 without effecting a transfer into the numeral wheel dials 26 of the second register. There being no transfer mechanism associated with the lower right-hand order of the ma- 13,5, 136 (Fig. 5), lever 128 chine, the tens-transfer into the second, or tens, order becomes effective immediately upon disengagement of the pilot gear 75 and the transfer into each successively higher order becomes sequentially operative thereafter. After 190 of each machine cycle, or 25 following the disengagement of the pilot gears for the one to four orders, and before the tens-transfer into the fourth order, pilot gears 75 associated with the remaining orders of the machine, are simultaneously disengaged to enable the sequential transfer into those dials 25 associated with these orders Without effecting a transfer into the corresponding dials 26.

As explained, the pilot gears 75 associated with each of the four lower orders, are disengaged simultaneously immediately following the digitation phase of each machine cycle, while those gears 75 associated with the remaining six higher orders of the machine, are simultaneously disengaged at 190 of each cycle. The disengagement and re-engagement of the pilot gears 75 in each group is controlled in pairs. A collar, indicated generally at 112, is provided for each pair of gears 75 and is secured on a shaft 113 (Figs. 3 and 4) slidably mounted at its forward end in transverse bracket 11 and at its rearward end in a boss secured to transverse bracket 15. Each shaft 113 has its axis paralleling the axes of shafts 72 and is positioned between each adjacent pair of shafts 72, so that each flange 74 of the associated pilot gears 75 engages in an annular groove 114 of collar 112. Each collar 112 is provided with spaced-apart flanges 115 between Which the circular end portion 116 of an upwardly extended arm 117 is positioned to control the forward and rearward movement of shaft 113 and the associated pilot gears 75.

Similar arms (Figs. 3, 4 and'S) are provided for each collar 112, with those arms 117 associated with the four lower orders being pinned to a shaft 118 journalled in brackets 119, 120 on transverse bracket 11, and those arms 117 associated with the three remaining pairs of ordinal shafts 72 being secured on a shaft 121 axially aligned with shaft 118 and journalled at its ends in brackets 122 and 123 on transverse bracket 11. It can be seen, therefore, that upon clockwise rocking movement of arms 117 (Fig. 3), shafts 113 are moved rearwardly to disengage the associated pilot gears 75 from the corresponding idler gears 76. To control the rocking movement of shaft 118, an arm 132 pinned thereon is provided with a bifurcation in the free end thereof engaging a roller 131 on an ear formed at a right angle to the free end of a lever 128 pivoted at 129 on transverse bracket 15. Lever 128 is also provided with an upwardly extended arm 133 on which a roller 134 is mounted for engagement with mentary cams, the other cam 136 of which pair of cams is maintained in cooperative engagement with a roller 137 carried by lever 128 in diametric opposition to roller 134. Cams and 136 are secured in spaced-apart relation on the rearwardly extended end of an actuator shaft 79 to accommodate the oscillatory movement of the lever 128 therebetween.

Immediately following clockwise rotation of cams is rocked counter-clockwise to impart a clockwise rocking movement to shaft 118 and therefore arms 117 (Fig. 3) to disengage the pilot gears 75 associated with the four lower orders of the machine. Each pair of pilot gears 75 associated with the fifth and sixth, seventh and orders, are similarly disengaged and re-engaged upon rocking of shaft 121. To rock shaft 121, a lever 138, similar to lever 128, is pivoted at 139 on transverse bracket 15 for oscillatory movement by a pair of complementary cams 140, 141 secured on an extended actuator shaft 79 and engaging respective rollers 142, 143 on lever 138, the roller 143 being oppositely disposed to roller 142 by mounting it on a vertically extended arm 144 of lever 138. At its free end, lever 138 is provided one cam 135 of a pair of compleeighth, ninth and tenth higher 7 with a laterally extended ear 145 on which is mounted a roller 146 engaging in a bifurcation in the free end of an arm 147 secured on shaft 121, which arm 147 is of the same conformation as arm'132.

Concurrent with the completion of the digitation phase, i.e., at 165 of each cyclic operation of the machine, the pilot gears 75 on the four lower order shafts 72 are simultaneously disengaged, and at 280 of each cycle are again re-engaged with their corresponding idler gears 76; whereas the pilot gears 75 associated with the remaining six higher order shafts 72 of the machine, are maintained in engagement until 190 of each cycle when they become disengaged and remain disengaged until the end of the cycle. As explained above, each ordinal shaft 72 is resiliently maintained in the rotated position thereof by the engagement of spring-urged ball 89 with the corresponding notch of the associated star wheel 88 during the disengagement of the related pilot gear 75. A series of similar spning-urged balls 150 (Fig. 3) are mounted in a bar 151 secured to transverse bracket 16 and serve, by engagement with the corresponding one of ten notches in a star wheel 152 on each of the ordinal shafts 78, to likewise maintain shafts 78 in the rotated positions thereof during the disengagement of the corresponding pilot gears 75.

A cyclically operable transfer mechanism is provided for the numeral wheel dials 26 of the second register CTl in cooperation with the actuating cylinders described above, and is simultaneously operable with, and independent of, the tens-transfer mechanism associated with the numeral wheel dials of the first register. The tripping means associated with each numeral wheel 26, excluding the highest order wheel, is of the same general type as that employed with the first register wheels 25, whereby the operation of the tripping means by alower order wheel, upon passing from 9 to 0 or 0 to 9, enables a transfer actuating mechanism to effect one increment of movement to the next higher order wheel. The sign character of the transferred increment is determined in the same manner as the sign character of the digitation increments.

Referring to Figs. 2, 3, 6, 7 and 8, the tripping of a transfer by each lower order numeral wheel 26 is effected by a single tooth gear 155 secured on each numeral wheel shaft 24 immediately below carriage frame 21 in cooperation with a tripping lever 156 pivoted at 157 in frame 21, each lever 156 being held therein by a springpressed ball in a manner similar to that employed for levers 93 associated with the first register dials 25. Lever 156 has an extension 158 positioned in the path of the single tooth gear 155 of one order, so that when the numeral wheel passes from 9 to O or 0 to 9, extension 158 is engaged by the tooth of gear 155 and the lever 156 is rocked in a clockwise direction, as viewed in Fig. 2. Lever 156 is also provided with an arm 159 extending into the next higher order of the machine and having an ear 160 extending downwardly and at right angles thereto for engagement with the face of an annular flange 161 integral with a ten-tooth transfer gear 162 secured to the forward end of a hub 163 slidably and nonrotatably mounted on shaft 78. At its rearward end, hub 163 carries a pair of spaced annular grooves 164 for cooperation with a spring-pressed ball 165 mounted in a transverse bar 166 which is maintained rigid and parallel with bar 151 on transverse bracket 16 by a plurality of spacer rods 167. Thus, in passing from 9 to 0 or 0 to 9, the tooth 155 on a lower order numeral wheel shaft 24, rocks the associated lever '156 to shift the corresponding hub 163 in the next higher order to position (gear 162 in operative relation with respect to the transfer actuator therefor. The gears 162 so positioned are maintained in active relation with the corresponding transfer actuators by virtue of the engagement of the spring-pressed.

balls 165 with the left-hand annular grooves 164, as viewed in Fig. 3.

A two-tooth cyclic transfer actuator gear 168 is provided for each transfer gear 162 and is pivotally mounted for oscillatory movement'on transverse bracket 15, with the axis of each actuating gear lying below and in the same vertical plane as to the axis of the corresponding transfer gear. Each two-tooth actuator 168 is provided with an arcual recessed portion 169 (Fig. 6) inthe periphery thereof, each end of which serves to limit the oscillatory movement of the actuator in either direction upon engagement with a pin 170 on transverse bracket 15' (Figs. 6, 7 and 8). A spring 171 normally urges actuator 168 in a counter-clockwise direction (Fig. 6) where the left-hand end of recess -169 abuts pin 170. In the counter-clockwise, or normal, position of actuator 168, the corresponding transfer gear 162 will have been moved forwardly of the machine or to the left, as viewed in Figs. 3 and 6, out of the plane of the actuator 168. Upon movement of gear 162 to operative position, the actuator 168 will be in position to immediately engage a tooth of the gear 162 upon clockwise rocking of the actuator. A V-shaped notch in the periphery of each actuator 168 provides a shoulder 172 for engagement by the extreme end of an associated laterally extended arm 173 of a lever 174 pivotally mounted on a transversely extended shaft 175 supported at its one end in a bracket 176 (Fig. 9) and at its other end and intermediate the ends thereof by similar brackets 177, all of which brackets are secured to transverse bracket 16.

A lever 174 is provided for each transfer actuator 168 to control the sequential operation thereof during the transfer phase of each machine cycle, thereby effecting a transfer into all register dials 26 from the second lowest order, or tens-order, dial to the highest, or fourteenth, order dial in which a transfer has been tripped. Referring to Fig. 11, it will be noted that the digitation phase of each machine cycle is completed in 165 of the cycle, whereupon the pilot gears 75 shiftable on the four lower ordinal shafts 72, are disengaged immediately to enable the initiation of the sequential operation of the tens-transfer mechanisms associated with each of the registers irrespective of the setting of plus-minus gears 40, 41 and/ or gears 45, 46. Upon initiation of the tens-transfer phase, a transfer is effected sequentially in each higher order dial of either or both registers during each succeeding 15 of each cycle. During the transfer into the hundredths order, or in 190 of the cycle, the pilot gears 75 associated with the fifth to the tenth higher order shafts 72 are disengaged, thus enabling an uninterrupted sequential operation of the tens-transfer mechanisms from the tensorder dials to the highest order dials in each register. Therefore, it is readily apparent that following the transfer into the tens, hundredths, and thousandths orders, that is, after 210 of the cycle, the pilot gears 75 associated therewith may be re-engaged. However, in the embodiment shown, the re-engagement of the gears 75 is effective after 280 of the cycle, while the remaining higher ordinal gears 75 do not become re-engaged until completion of the cycle.

Means are provided for sequentially rocking each transfer actuator 168 (Figs. 6, 7, and 8) to effect a transfer in each of the dials 26 from the dial aligned with the second lower keyboard order to the fourteenth dial to the left thereof, as viewed from. the front of the machine. An arm 180 of each lever 174 extends rearwardly of the machine through a rectangular aperture in transverse bracket 16, as seen in Figs. 3 and 9, and supports one end of a spring 181, the other end of which is suitably supported in the framework of the machine. Springs 181 serve to urge a depending portion 182 of each lever 174 into engagement with a corresponding cam 183 secured on a transverse shaft 184 supported in brackets 176 and 177 in axial parallel relation with shaft 175. Cam shaft 184 is cyclically driven in timed relation with actuator shafts 79 through a miter gear 185 (Fig. 9) secured on the rearward end of one of the shafts 79 and enmeshed with a miter gear 186 secured on one end of a driving shaft 187, one end of which is journalled in a bracket 188 secured on transverse bracket 15 and the other end of which is journalled in bracket 176 to maintain shaft 187 in axial parallel alignment with shaft 184. To drive shaft 184, shaft 187 carries a spur gear 189 enmeshed with a similar spur gear 190 secured to the outer end of shaft 184. Thus, for each cycle of rotation of actuator shafts 79, a cycle of rotation is imparted to shaft 184.

Viewing cam shaft 184 from the right side of the machine, from the left when viewed from the rear, as in Fig. 9, each suceeding cam 183 (Fig. from the lowest to the highest order cam, is angularly displaced approximately counter-clockwise from the adjacent lower order cam. Hence, each cam 183 becomes operative in sequence to effect a transfer into each adjacent higher order dial 26. The arcual lobe surface 195 of each cam 183 (Figs. 6, 7 and 8) is of sufficient length to maintain the associated lever 174 and transfer actuator 168 in the actively rocked position thereof, as seen in Fig. 7, so that the teeth of the actuator 168 positively block shaft 78 against further movement until transfer gear 162 associated therewith is restored to its inoperative position. To render each transfer gear 162 inoperative, a series of restore levers 196 are provided, one for each of the ten-tooth gears 162. Each lever 196 is rockably mounted on shaft 175 adjacent to, and cooperating with, a corresponding lever 174 as a unit. The semicircular end of an angularly disposed arm 197 of each lever 196 is normally maintained out of engagement with the rearward end of each transfer gear hub 163 (Figs. 3 and 6) by springs 198, each of which is supported at its upper end by an arm 199 of lever 196 extending laterally through the rectangular aperture in transverse bracket 16. At their lower end, springs 198 are secured to the framework of the machine.

A projection 200 is provided at the lower extremity of a depending arm 201 of each lever 196, which, under the urgency of spring 198, is maintained in contact with a corresponding one of a series of similar restore cams 202 secured in spaced relation on shaft 184 to control the rocking movement of the lever 196. The spacing between each restore cam 202 and a cooperating cam 183 is equivalent to the spacing between the corresponding levers 196 and 174 of each lever unit. Each cam 202 is angularly disposed on shaft 184 relative to the angular position of the adjacent cooperating cam 183 so that the associated restore lever 196 is rocked counter-clockwise (Fig. 8) to disengage transfer'gear 162 from transfer actuator 168 prior to the release of actuator 168 to its inactive position under the urgency of spring 171.

It is to be noted that during the transfer phase of each machine cycle, a transfer may be effected in all inboard order dials 26, except the units order dial, and in the four outboard order dials to the left, as viewed from the front of the machine. However, the transfer gears 162 in the four outboard orders are not restored to their inoperative position until the beginning of the ensuing cycle. The engagement of the transfer gears 162 in these four orders with the associated transfer actuators 168 does not, in any way, afiect the operation of the machine in the subsequent cycle, since there is no digitation mechanism associated with these four outboard orders to the left of the keyboard. In other words, at the end of a machine cycle the cam followers 174 and 196, in the lowest ten orders, will have passed from the lobes from their respective cams and the parts are restored to their normal position; while in the eleventh to fourteenth orders the cam followers will still be engaging the lobes of their respective cams, although adjacent the trailing edge thereof. The cam shaft 184, however, is driven in synchronism with the main drive shaft 82 of the machine, so that after the start of the next cycle, the cam shaft 184 starts rotating and immediately the cams are rotated from under the cam followers 174 and 196. If it should happen that the following cycle involves a carriage shifting operation there is ample time for the auxiliary transfer members in the outboard orders to be restored, as conventionally there is a lag of about 30 from the start of the cycle before the shifting mechanism starts operation, while only about 10 are required to restore the transfer members. If the following cycle happens to be a digitation operation, then there is an equal amount of time to permit the restoration of these transfer elements before digitation begins in the tenth order, for that may start at approximately the 48 position. Thus, in any event, the transfer mechanisms in the outboard orders are restored before any change in condition in the machine can begin in the following cycle.

The transfer operation in each of the thirteen order dials 26 is more clearly exemplified by the operation of the tens-transfer unit associated with the second, or tens order, dial 26, as indicated in Figs. 6, 7 and 8. In Fig. 6, the relative position of the operating portion of cams 183 and 202 is indicated with respect to the corresponding arm 182 and projection 200 of respective levers 174 and 196 in the full-cycle position of shaft 184. In Fig. 7, cam shaft 184 has been rotated in a clockwise direction and one increment of movement has been transmitted to shaft 78, and in Fig. 8 a further 60 rotation of shaft 184 has rendered cam 202 effective to rock lever 196 counterclockwise to restore transfer gear 162 to its inactive position, While the arcual lobe surface 195 of cam 183 is effective to maintain transfer actuator 168 in its operative, or clockwise, rocked position.

I claim:

1. In a calculating machine having two registers, a plurality of ordinally arranged numeral wheels in each of said registers, a plurality of differential toothed actuators for said registers, a cyclically operable drive means for said actuators, ordinally arranged means driven by said actuators to control registrations in one of said registers, an ordinally progressive tens-transfer mechanism for said one of said registers, ordinal means normally positioned for operation by said driven means to simultaneously control registrations in the other of said registers, ordinally arranged means rockable to render said normally positioned means ineffective, a first cam means driven by said cyclic drive means operable to rock certain orders of said rockable means to disable the operation of certain orders of said normally positioned means during the operation of the ordinally related tens-transfer mechanisms, and a second cam means driven by said cyclic drive means operable to rock the other orders of said rockable means to disable the operation of the other orders of said normally positioned means during the operation of the ordinally related tens-transfer mechanisms.

2. In a calculating machine having a register, a series of ordinal numeral wheels in said register, plus-minus gears for selectively transmitting positive and negative increments of movement to said numeral wheels, a series of ordinal shafts forcontrolling the rotation of said gears, and actuating means for driving said shafts, a normally inoperative gear for each of said shafts positionable thereon to control the rotation thereof, a vertical frame mem her, a plurality of two-tooth actuators, each pivoted on said frame about an axis parallel to the axis of each of said shafts and having its teeth disposed for engagement with the teeth of the corresponding one of said positionable gears in the operative position thereof, a transfer lever associated with each of said wheels and operable by a lower order wheel in passing from 9 to 0 or 0 to 9 to operatively position the said positionable gear in the next higher order relative to the corresponding one of said two-tooth actuators, a supporting shaft extending transversely of said ordinal shafts, a series of levers pivoted on said shaft, one for each of said actuators operable upon rocking thereof to rotate the corresponding actuator and the operatively positioned gear associated therewith for one'increment of movement, a cyclically controlled shaft driven by said actuating means and having its axis parallel to said supporting shaft, actuating elements rotatable by said driven shaft to control the rocking of said levers, a restore member for each of said positionable gears, each of said members being pivoted on said supporting shaft adjacent a corresponding lever, and a series of single-tooth gears angularly disposed on said driven shaft relative to said elements operable to rock the associated restore member to inoperatively position the corresponding positionable gear.

3. In a calculating machine, a series of ordinal numeral wheels, a gear for each of said wheels positionable from an inactive position for transmitting movement to said wheels, a tens-transfer mechanism operable by a lower order wheel to move the one of said gears associated with the adjacent higher order wheel from its inactive to active position, a toothed actuator for each of said gears operable to efiect an increment of rotation to the said higher order wheel subsequent to the operation of said tens-transfer mechanism, the combination comprising a spring means urging said actuator to an inoperative position, an actuating lever operable to impart a limited movement to said actuator, a restore lever for moving the higher order gear toits inactive position, a cyclically operable driving shaft, an arcual cam driven by said shaft for controlling said actuating lever, a second cam on said shaft having its operating portion angularly disposed relative to said first-mentioned cam for controlling said restore lever immediately following operation of the said toothed actuator, said first-mentioned cam having an arcual surface of sufficient length to maintain the said actuator in its operative position until disengagement of the said gear from the said actuator, a spring for urging said actuating lever to an inoperative position thereby enabling the operation of said actuator spring means, and a'second spring operable to move said restore lever to its inactive position as determined by said second cam.

4. In a calculating machine, a series of ordinal numeral Wheels, a gear for each of said wheels positionable from an inactive position for transmitting movement to said wheels, a tens-transfer-mechanism operable by a lower order wheel to move the one of said gears associated with the adjacent higher order wheel from its inactive to activeposition, a toothed actuator for each of said gears operable to effect an increment of rotation to the said higher order Wheel subsequent to the operation of said tens-transfer mechanism, a spring means urging said actuators to an inoperative position, actuating levers operable to impart a limited movement to said actuators, restore levers for moving each higher order gear to its inactive position, a cyclically operable driving shaft, a series of cams mounted on said shaft for controlling said actuating levers, a second series of cams on said shaft having their operating portion angularly disposed relative to a corresponding first-mentioned cam for controlling said restore levers immediately following operation of the said toothed actuators, said first-mentioned cams having an operating portion of suificient length to maintain the corresponding actuators in their operative position until disengagement of the said corresponding gear from its said actuator, springs for urging said actuating levers to an inoperative position thereby enabling the operation of said actuator spring means, and springs operable to move said restore levers to their inactive position as determined by said second earn.

5. A tens-transfer mechanism for a calculating machine having a series of ordinal numeral wheels and means for differentially driving said wheels which comprises a gear for each of said wheels positionable from an inactive position to an active position for transmitting movement to said wheels, a tens-transfer member operable by a lower order wheel to move the gear associated with the adjacent higher order wheel from its inactive to active position, a-toothed actuator for each of said gears operable to effect an increment of rotation to the said higher order-wheel, aspring means urging said actuators to an inoperative position, an ordinal series of actuating levers operable to impart a limited movement to said actuators, an ordinal series of restore levers for moving the higher order gear to its inactive position, a cyclically operable driving shaft, an ordinal series of cams on said shaft and having a prolonged operating portion operative subsequent to the operation of said differential driving means for controlling said actuating levers, a second ordinal series of cams on said shaft and having a short operating portion angularly disposed relative to a coordinal first-mentioned cam for controlling said restore levers immediately following operation of the said toothed actuators and before release of the coordinal actuating lever by the coordinal first-mentioned cam, a second spring means for urging said actuating levers to an inoperative position and thereby enabling the operation of said actuator spring means, and a third spring operable to move said restore lever to its inactive position as determined by said second cam.

6. In a calculating machine having a register, a series of ordinally arranged numeral wheels in said register, plus-minus gears for selectively transmitting positive and negative increments of movement to said numeral wheels, a series of ordinal shafts for controlling the rotation of said gears and actuating means for driving said shafts, the combination in each order which comprises a normally inoperative positionable gear slidably and nonrotatably mounted on the shaft of such order, a twotooth actuator pivoted about an axis parallel to the axis of said shaft and having its teeth disposed for engagement with the teeth of the said positionable gear when positioned in the plane of said actuator, a transfer lever operable by the wheel in passing through a tens-transfer position to position the said positionable gear in the next higher order in the plane of its two-tooth actuator, a lever operable upon rocking thereof to rotate the corresponding actuator for one increment of movement, an actuating element driven by saidactuating means to control the rocking of said lever, a restore member for said positionable gear, and a cam means angularly disposed relative to said element and operable to operate the associated restore member to position the positionable gear in its inoperative position.

7. In a calculating machine having two registers, a plurality of ordinally arranged numeral wheels in each of said registers, a plurality of ordinally progressive differential toothed actuators for said registers, a cyclical ly operable drive means for said actuators, ordinally arranged means driven by said actuators to control registrations in one of said registers during a digitation portion of each cycle, an ordinally progressive tens-transfer mechanism for said one of said registers operative during a transfer portion of each cycle, ordinal clutch means engaged with said driven means to simultaneously control registrations in the other of said registers, ordinally arranged disengaging means operable to render said clutch means inelfective, means driven by said cyclically operative drive means to operate certain orders of said disengaging means to disable the clutch means of those certain orders at the end of the digitation portion of the cycle in those certain orders and a second means driven by said cyclically operative drive means to operate the other orders of said disengaging means to disable the clutch means of the other orders at the end of the digitation portion of the cycle in the other orders, and a second tens-transfer mechanism progressively operable simultaneously with the corresponding orders of said iirstmentioned tens-transfer mechanism to effect transfers in said other of said registers comprising a normally inoperativetransfer gear for each of said register wheels operable to impart an increment of rotation thereto, a

2,908,441 13 14 transfer initiating means associated with each of said References Cited in the tile of this patent numeral wheels rendered effective by a lower order wheel ITED TATES PATENTS to enable the operation of the adjacent higher order gear, UN S a toothed actuator for each of said gears operable to efiect 897,659 Rem Sept 1908 he increment of rotation of the wheel associated there- 5 967,489 BauFrle 1910 with, actuating levers operable to impart an increment of 1'192721 Whit? July 1916 movement to said actuators, an ordinal series of restore 1231999 Burdlck July 1917 levers for moving the gears to their inactive position, 1,900,776 Suter 1933 cam-operated means for sequentially controlling the op- FOREIGN PATENTS eration of said actuating levers and thereafter said re- 10 store levers subsequent to the operation of said disen- 23,575 Great Bntam J1me 1915 gaging means, and resilient means for restoring said ac- 2 Germany Feb. 8, 1922 tuating levers and said restore levers to their inoperative 19,176 Germany Feb. 25, 1931 positions. 760.102 Germany Jan. 11, 1954 

